EP0213948B1 - Öldruck-Regelsystem für stufenloses Getriebe - Google Patents

Öldruck-Regelsystem für stufenloses Getriebe Download PDF

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Publication number
EP0213948B1
EP0213948B1 EP86306702A EP86306702A EP0213948B1 EP 0213948 B1 EP0213948 B1 EP 0213948B1 EP 86306702 A EP86306702 A EP 86306702A EP 86306702 A EP86306702 A EP 86306702A EP 0213948 B1 EP0213948 B1 EP 0213948B1
Authority
EP
European Patent Office
Prior art keywords
control valve
line pressure
spool
transmission
pressure control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP86306702A
Other languages
English (en)
French (fr)
Other versions
EP0213948A1 (de
Inventor
Yoshihiko Morimoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Subaru Corp
Original Assignee
Fuji Jukogyo KK
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Fuji Jukogyo KK filed Critical Fuji Jukogyo KK
Publication of EP0213948A1 publication Critical patent/EP0213948A1/de
Application granted granted Critical
Publication of EP0213948B1 publication Critical patent/EP0213948B1/de
Expired legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F16H61/66254—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling
    • F16H61/66259—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling using electrical or electronical sensing or control means

Definitions

  • a further known control system for a continuously variable belt-drive transmission disclosed in United States Patent No. 4,369,675 comprises an endless belt running over a drive pulley and a driven pulley.
  • Each pulley comprises a movable conical disc which is axially moved by a fluid operated servo device so as to vary the running diameter of the belt on the pulleys in dependence on driving conditions.
  • the system is provided with a hydraulic circuit including a pump, a first spool valve for line pressure control and a second spool valve for transmission ratio control.
  • Japanese Patent laid Open 58-88252 discloses moreover a transmission control system provided with a torque motor for operating a line pressure control valve in accordance with engine torque and transmission ratio so as to control line pressure.
  • the system is arranged to control the line pressure to reduce as the engine torque decreases.
  • the continuously variable belt-drive automatic transmission for a motor vehicle to which the present invention is applied comprises an electromagnetic powder clutch 2 for transmitting the power of an engine 1 to transmission 4 through a selector mechanism 3.
  • a drive gear 12 Secured to the output shaft 6 is a drive gear 12 which engages with an intermediate reduction gear 13 on an intermediate shaft 14.
  • An intermediate gear 15 on the shaft 14 engages with a final reduction gear 16.
  • the rotation of the final reduction gear 16 is transmitted to axles 18 of a vehicle driving wheels 19 through a differential 17.
  • the hydraulic control circuit 20 includes a line pressure control valve 40 and a transmission ratio control valve 50.
  • the line pressure control valve 40 comprises a valve body 41, spool 42, and ports 41 a, 41 b, 41 c, 41 d, 41 e and chambers 41f and 41g.
  • the chamber 9 of the drive pulley 7 is applied with pressurized oil by an oil pump 21 from an oil reservoir 26 passing through a line pressure conduit 22, ports 41a and 41e of line pressure control valve 40, transmission ratio control valve 50, and conduit 23.
  • the chamber 10 of driven pulley is supplied with pressurized oil through a passage 22b without passing through valves 40 and 50.
  • the movable conical disc 7a of the drive pulley 7 is so designed that the pressure receiving area thereof is larger than that of movable conical disc 8a of the driven pulley 8.
  • the spool 42 is supplied with pressurized oil supplied to a chamber communicating with port 41c through a conduit 36.
  • the spool 42 is urged towards the left by the force of a spring 43 provided between the end of the spool and a retainer 45 the position of which is adjustable by a screw 44.
  • the port 41 a is connected with port 41 b of a drain passage 27 in accordance with the position of a land of the spool 42.
  • the system of the present invention is provided with a pressure reducing valve 60, and solenoid operated on-off control valves 65 and 67.
  • the pressure reducing valve 60 comprises a valve body 61, spool 62, inlet port 61 a, basic pressure port 61b, drain port 61c, end chamber port 61d, spring 63 urging the spool 62 toward an end chamber 61e.
  • the basic pressure port 61b is positioned between the inlet port 61a and drain port 61c, and the spring 63 is positioned opposite the end chamber 61e against the regulator pressure.
  • the load of the spring 63 can be adjusted by an adjust screw 64.
  • the port 61 a is connected to the pump 21 through a conduit 31 having an orifice 32 branched from conduit 22, and ports 61 b and 61 d are connected to a conduit 33.
  • the spool 62 is shifted to the right by spring 63, so that port 61 a communicates with port 61b to increase the pressure in the conduit 33.
  • a constant basic pressure of oil which is lower than the line pressure is provided in the conduit 33.
  • the conduit 33 is communicated with the port 41d of line pressure control valve 40 through an orifice 34 and a passage 37.
  • the conduit 33 is also communicated with reservoir 26 through solenoid operated on-off valve 65 and with an accumulator 66. Further, the conduit 33 is communicated with an end chamber 51f of the port 51d of the transmission ratio control valve 50 through a passage 53 and with another end chamber 51g of a port 51e through a passage 54 having an orifice 35.
  • the solenoid operated on-off valve 67 is connected to the passage 54 at the downstream of orifice 35 so as to drain the oil in the chamber of the drive pulley to the reservoir 26.
  • the solenoid operated valve 65 is adapted to be operated by pulses.
  • the transmission ratio changing speed (di/dt) is a function of flow rate Q of oil supplied to the chamber 9, and the flow rate Q is a function of duty ratio D, line pressure PL and primary pressure P ⁇ in the chamber 9, namely:
  • the duty ratio D can be obtained from the speed.
  • the actual transmission ratio i is larger than the desired transmission ratio id (i>id)
  • the value of di/dt is negative.
  • the duty ratio D is increased to reduce the pressure in the chamber 51g g so as to upshift the transmission.
  • the downshift is performed in the reverse manner.
  • the system is provided with a drive pulley speed sensor 71, driven pulley speed sensor 72, throttle valve position sensor 73, engine speed sensor 74 and idle switch 86.
  • the output signals N s of the sensor 72 and the output signal 8 of the throttle valve position sensor 73 are fed to a desired transmission ratio table 76.
  • the desired transmission ratio id is fetched from the table in accordance with the signals N s and ⁇ .
  • the speed di/dt and actual ratio i are applied to a duty ratio table 79 to derive the duty ratio D of pulses for control valve 67.
  • the duty ratio in the table 79 decreases with increases of speed di/dt and ratio i.
  • the duty ratio D is supplied to the solenoid operated valve 67 through a driver 80.
  • the actual ratio i is applied to a necessary line pressure setting section 82 which produces a necessary line pressure PL u from a graph.
  • the desired line pressure PL is applied to a duty ratio table 84 through a line pressure correcting section 89 to produce a duty ratio DP dependent on the desired line pressure.
  • the duty ratio DP is applied to the solenoid operated valve 65 through a driver 85.
  • an idle switch 86 detecting the idle operation of the engine is provided in order to detect the coasting of the vehicle, and a calculating section 87 is provided for calculating the magnitude of deceleration based on the output signal N s of driven pulley speed sensor 72.
  • the magnitude G is calculated as follows. where N s xn is the output signal of the driven pulley speed sensor 72 at a time in the operation cycle, and N s xn-1 is the output signal of the sensor at the last time of the operation cycle.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Transmission Device (AREA)
  • Control Of Driving Devices And Active Controlling Of Vehicle (AREA)

Claims (2)

1. Getriebe-Steuersystem für ein Kraftfahrzeug mit einem stufenlos verstellbaren Getriebe und einer Kupplung (2); bei dem das Getriebe folgende Teile hat:
ein Antriebsrad (7) und ein Abtriebsrad (8), die beide je eiene hydraulisch verschiebbare Scheibe (7a, 8a) sowie entsprechende Zylinder (9a, 6a) zum Verschieben der zugeordneten Scheibe aufweisen,
einem um beide Räder geschlungenen Riemen (11),
ein mit einem Schiebar versehenes Leitungsdruck-Steuerventil (40),
ein mit einem Schieber versehenes Übersetzungsverhältnis-Steuerventil (50),
einen Hydraulikkreis mit einer Pumpe (21) zum Zuführen von Öl an den Zylinder des Antriebsrades über das Leitungsdruck-Steuerventil und das Übersetzungsverhältnis-Steuerventil,
eine Verteilereinrichtung (31), die sich von dem Hydraulikkreis aus verzweigt und das Leitungsdruck-Steuerventil mit Öl versorgt, und die mit einem Druckregelventil (60) zum Aufrechterhalten eines konstanten Öldrucks sowie mit einem elektromagnetisch betätigten Steuerventil (65) zum Steuern der dem Leitungsdruck-Steuerventil zugeführten Ölmenge zwecks Verschiebung des Schiebers versehen ist, wobei Schiebebetrieb des Fahrzeugs berücksichtigt wird; dadurch gekennzeichnet, daß
ein Leerlaufschalter (86) vorgesehen ist, mit dem der Zustand festgestellt wird, in dem das Fahrzeug im Schiebebetrieb arbeitet, und mit dem ein Schiebebetriebsignal erzeugt wird;
daß ein Sensor (72) zum Erzeugen eines Fahrgeschwindigkeitssignals sowie
eine Recheneinrichtung zum Erzeugen eines Verzögerungssignals abhängig von dem Fahrzeuggeschwindigkeitssignal vorgesehen sind; und
daß das Schiebebtriebsignal und das Verzögerungssignal elektronischen Mitteln (88, 89) zugeführt werden, um das elektromagnetisch betätigte Steuerventil (65) zu betätigen, so daß der Schiebar (42) des Leitungsdruck-Steuerventils (40) zur Erhöhung des Leitungsdruckes in Übereinstimmung mit dem Verzögerungssignal verschoben wird.
2. Steuersystem nach Anspruch 1, dadurch gekennzeichnet, daß das Steuerventil ein elektromagnetisch betätigtes Ein-Aus-Ventil ist.
EP86306702A 1985-08-30 1986-08-29 Öldruck-Regelsystem für stufenloses Getriebe Expired EP0213948B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP60191049A JPS6252264A (ja) 1985-08-30 1985-08-30 無段変速機の油圧制御装置
JP191049/85 1985-08-30

Publications (2)

Publication Number Publication Date
EP0213948A1 EP0213948A1 (de) 1987-03-11
EP0213948B1 true EP0213948B1 (de) 1989-06-28

Family

ID=16268038

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86306702A Expired EP0213948B1 (de) 1985-08-30 1986-08-29 Öldruck-Regelsystem für stufenloses Getriebe

Country Status (4)

Country Link
US (1) US4730522A (de)
EP (1) EP0213948B1 (de)
JP (1) JPS6252264A (de)
DE (1) DE3664154D1 (de)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2541821B2 (ja) * 1987-06-30 1996-10-09 富士重工業株式会社 無段変速機の変速制御装置
JPS6444394A (en) * 1987-08-11 1989-02-16 Honda Motor Co Ltd Controller for non-stage transmission
EP0313275B1 (de) * 1987-10-19 1994-01-12 Honda Giken Kogyo Kabushiki Kaisha Verfahren zur Steuerung des Übersetzungsverhältnisses eines stufenlos veränderlichen Getriebes
JPH07117159B2 (ja) * 1987-11-05 1995-12-18 本田技研工業株式会社 車両用無段変速機の変速制御方法
JP2794703B2 (ja) * 1987-12-24 1998-09-10 日産自動車株式会社 無段変速機の変速制御装置
DE3844872C2 (de) * 1987-12-24 1996-05-15 Nissan Motor Verfahren und Einrichtung zur Steuerung des Übersetzungsverhältnisses eines Kegelscheiben-Umschlingungsgetriebes
JPH0792138B2 (ja) * 1988-03-01 1995-10-09 日産自動車株式会社 自動変速機のライン圧制御装置
JPH02212670A (ja) * 1989-02-10 1990-08-23 Honda Motor Co Ltd 変速機のクラッチ制御装置
JPH0454366A (ja) * 1990-06-22 1992-02-21 Jatco Corp 自動変速機の制御装置
JP2636582B2 (ja) * 1991-08-01 1997-07-30 日産自動車株式会社 トロイダル無段変速機の制御装置
JP3394462B2 (ja) * 1998-11-26 2003-04-07 株式会社日立製作所 自動変速機の制御装置及び制御方法
US6099424A (en) * 1998-12-30 2000-08-08 Hamilton Sundstrand Corporation Continuously variable transmission with control arrangement and method for recovering from transmission belt slipping
US6174254B1 (en) 1998-12-30 2001-01-16 Hamilton Sundstrand Corporation Continuously variable transmission with control arrangement and for reducing transmission belt slippage
US6290620B1 (en) 1999-06-25 2001-09-18 Hamilton Sundstrand Corporation Continuously variable transmission with control arrangement and method for reducing impact of shock load
JP5039819B2 (ja) * 2010-09-01 2012-10-03 ジヤトコ株式会社 コーストストップ車両及びコーストストップ方法
EP2977649B1 (de) * 2013-03-22 2020-06-24 Jatco Ltd Stufenloses riemengetriebe
WO2017043458A1 (ja) * 2015-09-09 2017-03-16 ジヤトコ株式会社 車両用無段変速機構の制御装置および制御方法

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2145785A (en) * 1983-08-31 1985-04-03 Fuji Heavy Ind Ltd A system for controlling the transmission ratio of an infinitely variable belt-drive transmission

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL7811192A (nl) * 1978-11-13 1980-05-16 Doornes Transmissie Bv Werkwijze en inrichting voor het regelen van een trap- loos variabele transmissie van een motorvoertuig.
US4350234A (en) * 1979-02-02 1982-09-21 Nissan Motor Co., Ltd. Automatic transmission system provided with a function of engine brake
US4284096A (en) * 1980-06-04 1981-08-18 Ford Motor Company Automatic transmission governor having deceleration sensitive pressure switching feature
US4458318A (en) * 1981-04-24 1984-07-03 Borg-Warner Corporation Control arrangement for a variable pulley transmission
US4522086A (en) * 1981-04-24 1985-06-11 Borg-Warner Corporation Control system for continuously variable transmission
JPS5888252A (ja) * 1981-11-20 1983-05-26 Nissan Motor Co Ltd Ｖベルト式無段変速機のライン圧制御方法
DE3375598D1 (en) * 1982-04-30 1988-03-10 Nissan Motor Apparatus for controlling line pressure in continuously variable transmission
DE3370679D1 (en) * 1982-09-22 1987-05-07 Borg Warner Hydraulic control system for continuously variable transmission
JPH066974B2 (ja) * 1982-10-22 1994-01-26 日産自動車株式会社 Ｖベルト式無段変速機の油圧制御装置
GB2138895B (en) * 1983-04-29 1987-04-15 Aisin Warner Pressure regulating system for use in an automatic transmission
JPS6060361A (ja) * 1983-09-10 1985-04-06 Fuji Heavy Ind Ltd 無段変速機のライン圧制御装置
JPS6095263A (ja) * 1983-10-29 1985-05-28 Mazda Motor Corp 無段変速機の制御装置
JPS60132161A (ja) * 1983-12-21 1985-07-15 Fuji Heavy Ind Ltd 無段変速機の変速比検出装置
GB2152162B (en) * 1983-12-29 1987-09-23 Aisin Warner Control system for an automatic continuously variable transmission for a vehicle
US4619629A (en) * 1984-05-03 1986-10-28 Toyota Jidosha Kabushiki Kaisha Hydraulic pressure control apparatus for a continuously variable transmission
US4631043A (en) * 1984-05-03 1986-12-23 Toyota Jidosha Kabushiki Kaisha Hydraulic control apparatus for a continuously variable transmission

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2145785A (en) * 1983-08-31 1985-04-03 Fuji Heavy Ind Ltd A system for controlling the transmission ratio of an infinitely variable belt-drive transmission

Also Published As

Publication number Publication date
US4730522A (en) 1988-03-15
JPH0548390B2 (de) 1993-07-21
JPS6252264A (ja) 1987-03-06
EP0213948A1 (de) 1987-03-11
DE3664154D1 (en) 1989-08-03

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